Power reset wringer



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Oct. 16, 1956 B. R. THIELE 2,756,504

POWER RESET WRINGER Filed Nov. 10, 1952 6 Sheets-Sheet 4 mo Bev-t'hal ol Q. *rmLelve A; M, Ww.-%

dl-rw'onmayw Oct. 16, 1956 B. R. THIELE POWER RESET WRINGER 6 Sheets-Sheet 5 Filed NOV- lO, 1952 Q m Wm N r 6 A? llnited States Patent O POWER RESET WRINGER Berthold R. Thiele, Ripon, Wis., assignor to Speed Queen Corporation, Ripon, Wis., a corporation of Delaware Application November 10, 1952, Serial No. 319,690

8 Claims. (Cl. 68-253) The present invention pertains to power operated rollertype wringers for domestic laundry machines and relates particularly to wringers of this type having disabling means for quickly releasing the squeezing pressure from the wringer rollers and equipped with power actuated resetting means operable to restore the rollers into mutual engagement under pressure. Wringers of this general design are fully disclosed in my copending application Serial No. 219,062, filed April 3, 1951, now Patent No. 2,734,371, granted February 14, 1956.

It is one object of the invention to provide a wringer of the above type with an improved disabling mechanism which positively and substantially simultaneously disconnects the squeezing rollers from the power drive and releases the rollers for separation from each other in response to the primary action of a single control movement by the operator. A further and more specific object is to provide a wringer with a disabling mechanism of the above character which is so contrived that the simultaneous actions of the mechanism in de-energizing and separating the rollers are as an added safety feature executed independently of each other.

Another object is to provide a wringer with an improved power operated roller resetting mechanism which is inherently sensitive to the presence of objects of substantial size remaining between the rollers during a roller resetting cycle to automatically cut short the resetting action and return the rollers to a fully disengaged condition. A related and more particular object is to integrate into a wringer roller resetting mechanism of this character means which effectually cut short the energization of the rollers in the event the roller resetting cycle is automatically turned back in the manner recited.

An additional object is to provide a wringer of the foregoing character with improved transmission means for driving the wringer rollers selectively in opposite directions of rotation.

Other objects are to provide collateral advantages and safety features embodied in the exemplary form of the invention ShOWn in the drawings, in which:

Figure 1 is a front elevation, partially in section, of a wringer embodying the preferred form of the invention. As shown, the wringer is in disabled condition with the wringer rollers de-energized and separated from each other.

Fig. 2 is a fragmentary vertical sectional view taken along line 2-2 of Fig. 1.

Fig. 3 is a fragmentary horizontal sectional view taken along line 3-3 of Fig. 2 and showing the disabling control in displaced position.

Fig. 4 is a fragmentary vertical sectional view taken along line 4- of Fig. 1.

Fig. 5 is a fragmentary vertical sectional view generally similar to the sectioned portion of Fig. 1, but showing on an enlarged scale the relative positions of the structural components of the wringer operating mechanism when the wringer is in normal operation.

Fig. 6 is a fragmentary vertical sectional view taken along line 6-6 of Fig. 5 and showing in phantom the relationship of the resetting cam and its follower at the completion of the roller resetting movement.

Fig. 7 is a fragmentary vertical sectional view taken along line 7-7 of Fig. 5.

Fig. 8 is a fragmentary horizontal sectional view taken along line 8-8 of Fig. 5. This view is generally similar to Fig. 3, butvshows the relationship of the parts during the operative, rather than the inoperative, condition of the wringer.

Although certain advantages are realized from the specific correlation of structural elements and mechanisms incorporated into the preferred form of the invention shown, and described herein, it will be understood that the invention is not limited to this specific embodiment but embraces equivalent constructions falling within the spirit and .scope of the invention as expressed in the appended claims.

Referring again to .the drawings, particularly Fig. l, the wringer 10 constituting the exemplary embodiment of the invention comprises a horizontally elongated rectangular frame 11 disposed generally in a vertical plane and supported at one end (at the right in Fig. 1) from a power driven, domestic laundry machine (not shown). Two coacting squeezing rollers 12, 14 journaled in the frame 11 are rotated in either direction by means of a vertical drive shaft 15 at the supported end of the frame and connected to the lower roller 12 through the intermedium of an improved reversing clutch mechanism 16. As shown, the lower squeezing roller 12 is journaled at opposite ends in a lower horizontal base section 17 of the frame 11. The upper roller 14 is journaled at opposite ends in vertically floating bearings 24 slidably disposed in a pair of spaced depending legs 19 of a movable U-shaped head 20 constituting an upper horizontal section of the frame 11. Opposite ends of the head 20 are, in turn, supported on two spaced stationary elements of the frame 11, an upright end cap 21 at the free end of the frame and a hollow control mechanism housing 22 at the supported frame end. With the head 20 in is operating position (Fig. 5), a position somewhat lower than that shown in Fig. 1, the upper roller 14 is biased into yieldable engagement with the lower roller 12 by upright helical springs 25 acting downwardly from the upper portion of the head onto the upper roller bearings 24.

To provide for quick disengagement of the two squeezing rollers 12, 14 in emergencies when the hand of the user, or the like, may inadvertently become caught between the rollers, the roller support head 20 is shiftably mounted on its supports for movement between its operating position and a raised or inoperative position, Fig. l, in which the upper roller 14, carried by the head, is moved away from its companion lower roller 12.

The present invention is directed generally to an improved roller operating and control mechanism incorporated into the wringer 10 to provide, first, for substantially simultaneous de-energization and separation of the rollers 12, 14 and, secondly, for concurrent re'energization and power re-engagement of the rollers. This mechanism is actuated primarily by energy diverted from the drive shaft 15 and is, in the present instance, contained largely within the housing 22 at the supported end of the wringer.

As shown in Figs. 1 and 5, the roller operating and control mechanism includes a mechanical transmission comprising the reversing clutch 16 used to interconnect the vertical drive shaft with the lower roller 12 for rotating the latter selectively in either direction. Leading to the clutch 16 the drive shaft 15 protrudes into the control mechanism housing 22 through a bearing 26 at the lower end of the housing. A pinion gear 27 fixed to the extreme upper end of the shaft 15 meshes on opposite sides with two opposed cup gears 29 journaled for free counter-rotation on a rotary spindle 30 coaxial with the lower wringer roller 12. In this instance, the end of the spindle 30 adjacent the roller 12 is supported in a bearing 31 mounted in an upright support member 34 medially disposed within the housing 22. The opposite end of the spindle 31 is journaled in a bearing 32 recessed into the inner face of a cap 35 covering the otherwise open end of the housing 22 remote from the wringer rollers. A rotary driving connection between the spindle 30 and the lower roller 12 is made by a coupling 36 between the spindle and the adjacent one of two stub axles 37 projecting from opposite ends of the roller and journaled in the base section 17 of the wringer frame 11.

To drive the roller 12 selectively in either direction, the transverse spindle 30, connected to the roller 12, is clutched into driven engagement withthe appropriate one of the counterrotating cup gears 29. As shown in Fig. 5, the cup gears 29 are individually clutched to the spindle 30 by two independently acting spring clutches 39. These clutches operate to connect the respective cup gears 29 to an elongated cylindrical sleeve 40 coaxial with the spindle 30 and fixed thereto between the two gears by means of a central apertured web 41 pinned to the spindle. Opposite ends of the sleeve 40 are recessed to define cylindrical wells 42 concentric about the spindle 30. The hub 44 of each cup gear 29, which is journaled in the spindle 30 by means of an internal bearing 45, is extended axially into the well 42 at the adjacent end of the sleeve 40 to define with the inner cylindrical wall of the well an axially elongated annular space 46 for the accommodation of a closely coiled helical spring clutch element 47.

To effect a driving connection between each spring clutch element 47 and the respective cup gears 29, the longitudinal end of the spring element adjacent the web of the coacting gear is extended into an annular recess 49 in the base of the gear and the extreme end of the spring convolution at the bottom of the recess is engaged with an axially stepped abutment 50 on the gear base. Each spring clutch element 47 when unstressed tends to contract around an axial bushing 51 interposed between the clutch element and the elongated hub extension of the associated cup gear 29. The radial thickness of each spring clutch element 47 is such that when the element is free to assume its contracted state, its outer diameter shrinks to a size less than that of the cylindrical wall of the sleeve Well 42 overlying the clutch element, thereby releasing the clutch element and its associated cup gear 29 from the sleeve 40.

To establish a cushioned but firm clutching engagement of a selected one of the cup gears 29 with th spindle 30, the torque transmitting spring element 47 of the coacting one of the clutches 39 is caused to swell radially outward to establish a strong frictional engagement with the cylindrical Wall of the contiguous sleeve well 42. This swelling action of the spring clutch element 47 is induced by retarding rotation of the end of the spring element remote from its driving gear 29, the spring element being coiled in a direction to be self-expanding in response to drag tending to restrain its free turning movement by the gear.

The engagement of a selected one of the clutches 39 as a consequence of the application of a retarding torque to the normally free end of the spring element 47 of the clutch is, therefore, attended by a substantial though limited forced uncoiling of the spring element. The consequent ability of this spring element 47 to absorb a significant amount of mechanical energy as an incident to engagement of the selected clutch 39 is efiectually utilized to cushion the starting of the wringer rollers. Thus, to effect a cushioned engagement of either of the counter-rotating cup gears 29 with the lower roller 12 selector means is provided to positively engage the nortmally free end of the spring clutch element 47 of the selected gear with the intermediate sleeve 40. For this purpose an annular selector collar 52 is slidably mounted on the sleeve 40 for axial shifting movement to either side of a neutral position centered with th sleeve web 41. A pilot pin 54 fixed to the inner surface of the selector collar 52 projects radially inward into a longitudinal slot 55 in the sleeve 40. When the selector collar 52 is in neutral position, the pilot pin 54 registers with the sleeve web 41. Upon longitudinal movement of the collar 52 toward the clutch 39 to be engaged, the pilot pin 54 is carried into one of a series of circumferentially spaced notches 56 defined by a broken annular flange 58 formed on the end of the associated clutch bushing 51 adjacent the sleeve web 41. The pin interlocks the sleeve 40 with the bushing 51 of the selected clutch. This bushing is anchored to the end of the encircling spring clutch element 47 remote from the associated driving gear 29. Thus, the yieldable spring clutch element forms a cushioned initial connection between the selected gear 29 and the roller 12. Thus, the cushioned torque of the spring clutch element 47 acting on the sleeve 40 incident to the engaging action of the clutch greatly minimizes the impact of connecting the selected driving gear 29, turning at full speed, with the stationary roller 12 and associated structural elements. The continuing resistance of the roller 12 to rotation acts on the sleeve web end of the spring clutch element e7 of the selected clutch 39 to expand the clutch element into tight frictional clutching engagement with the cylindrical drum surface of the adjacent sleeve well 42.

To disengage the lower roller 12 from the power drive, the selector collar 52 and the attached pilot pin 54 are shifted back to neutral position midway of the sleeve 40 gaging positions is effected by manual actuation of one of two companion push button controls 57, 59 accessibly located on the control mechanism housing 22 and corresponding respectively to the reverse directions of rotation of the wringer rollers 12, 14. As shown in Figs. 1 and 5, the push buttons 57, 59 are formed on the outermost ends of two horizontal plungers 60, 61 slidably mounted in the housing 22 in over and under relation to each other for reverse reciprocation longitudinally of the frame 11. From their outer control button ends which slidably protrude through the end cover 35 of the housing 22, the plungers 60, 61, disposed above the reversing clutches 39, extend through the housing longitudinally of the frame 11 into apertures 62, 64 defined in an upward extension of the support member 34. The upper plunger 60 is interconnected with the lower plunger 61 by a cross link 65 connected at opposite ends by pin and slot pivots 68 to the respective plungers and medially pivoted to the housing 22. Hence, the upper plunger can be shifted either inwardly by manual pressure on the upper button 57 or outwardly by manual pressure on the lower button 59 transmitted reversely to the upper plunger 60 by the cross link 65.

Reverse control movements of the upper plunger 60 are yieldably transmitted to the selector collar 52 for the reversing clutches 39 by an upright rocker link 66. This link is medially pivoted to the support 34 just above the clutches 39 and is articulated at its lower end with an annular groove 67 defined on the periphery of the selector collar 52. The upper end of the rocker link 66 is resiliently connected to the upper plunger 60 whereby a clutch engaging motion of the latter serves to bias the pilot pin 54 into smooth engagement with the bushing flange 58 of the selected one of the clutches 39. In this instance the resilient connection between the link 66 and the plunger 60 is made by two opposed helical springs 69 disposed within the plunger which is of a hollow construction. The springs are attached respectively to two spaced anchors 70 on the plunger to exert a resilient centering action on a transverse pin 71 fixed to the upper end of the rocker link 66 and projecting into the plunger through an elongated slot 73.

To assure that the selector collar 52 will not drift into and out of its clutch engaging positions, detent means is correlated with the cross link 65 between the plungers 6t), 61 to yieldably retain the selector linkage in the position to which it is positively shifted. In this instance, the outer elongated edge of the cross link 65 is shaped to form three adjacent indentations 72 having angular spacings around the central link pivot corresponding to the three angular stations of the link. Yieldable retention of the link 65 in its various angular stations is effected by engagement of the respective indentations 72 with a spring pressed pin 74 slidably mounted in the housing cover plate 35.

Reverting now to the shiftable means used to support the head 20 alternatively in a lowered position in which the upper roller 14 is operatively engaged with the lower roller 12 and a raised inoperative position in which the roller 14 is separated from its companion roller to release objects inadvertently caught between the rollers, it will be observed from Figs. 1 and 5 that the head 20 is supported directly on rock shaft means 75 extending longitudinally through the bridge of the head between two shaft bearings 76 mounted respectively in the wringer frame end cap 21 and a vertical bulkhead 78 in the roller end of the control mechanism housing 22. In this instance, the rock shaft 75 is equipped with a pair of matched eccentric shifting disks 77 longitudinally spaced along the shaft and rotatably disposed in bearings 79 at opposite ends of the head 20 whereby reverse rotary rocking movements of the shaft effect vertical shifting of the head between its operative and inoperative posi= tions.

Upon downward movement of the head 20 into its operative position (Fig. 5) effected by forward rota- L on of the rock shaft 75 (clockwise with reference to Fig. 2), the shaft is latched against reverse rotation to prevent upward displacement of the head. The im proved latching means provided for this purpose is disposed within the control mechanism housing 22 for coacting with the adjacent end of the rock shaft 75 which projects into the housing. As shown in Figs. 5 and 7, the latching means comprising a generally vertical latching plate 39 is pivoted at its upper end between lug brackets 81 on the housing 22 above the shaft 75. From its support lugs the latching plate 85 extends downwardly across the shaft and is centrally apertured 82 to rotatably receive the contiguous end of the shaft. A spring 84 acting between the housing 22 and the latching plate 80 biases the latter about its pivotal axis, which extends transversely of the rock shaft 75, toward a coacting latching collar 85 encircling the shaft and anchored for rotation therewith by opposite ends of a locking pin 86 projecting radially from the shaft into axial slots 87 formed in the hub of the collar. A latching fin ger 89 anchored to the marginal edge of the collar 85 projects into a radial extension 90 of the central plate aperture 82 to engage a ledge 91 at one side of the extension and lock the collar and rock shaft 75 against reverse or roller parting movement (counterclockwise with reference to Fig. 7).

In addition to the previously described control means for engaging the power clutches 39 selectively, second wringer control means, conveniently operable from either side of the frame 11, are provided for simultaneously separating the rollers 12, 14 from each other and positively disengaging the rollers from the power shaft 15 by the primary action of a single control movement of the operator.

As shown in Figs. 3, 5, 7, and 8, the illustrated form of the double action means used to quickly terminate the squeezing action of the wringer in emergencies or otherwise comprises a reciprocable control plunger 92 extending transversely through the medial portion of the control mechanism housing 22 at the wringer roller side of the upright support 34. Opposite ends of the plunger 92 pierce the opposed sides 95 of the housing 22 and are fitted with mushroom type pressure heads 94. Normally, the plunger 92 is resiliently maintained in a centered position with the two pressure heads 94 disposed substantially equal distances from the adjacent housing walls 95. For this purpose, two opposed helical springs 96 are coiled about the plunger to act respectively between two spaced abutments 97 on the plunger and an apertured bracket 99 on the housing 22 which slidably receives the medial section of the plunger.

Longitudinal shifting movement of the plunger 92 to either side of its mid-position (Fig. 3) by manual force applied to either of the pressure heads 94 is transmitted to a multipurpose intermediate control element 100. As shown in Figs. 3, 5, 7, and 8, the control element 100 comprises a spool 101 supported for reciprocable movement longitudinally of the wringer frame 11 by means of a longitudinally floating pin 102 disposed between the extended axes of the clutch control plungers 60, 61 in parallel relation thereto. In the present construction, one end of the pin 102 is slidably received in an aperture 104 formed in the upright support 34 parallel to and midway between the control plunger apertures 62, 64. From the support 34 the pin 102 extends over the plunger 92 and continues through a second support aperture 105 (Fig. 5) defined in the housing bulkhead 78.

Str'uctur'ally, the means employed in this instance to transmit control movements of the disabling plunger 92 to the spool 101 comprises a cam actuated lever 106 formed by a U-shaped stamping including a pair of spaced legs 107 (Figs. 7 and 8) pivoted to the housing 22 at one end of the plunger and extending toward the spool generally along the side of the plunger adjacent the clutch control plungers 6t), 61. When the plunger 92 is in its central position, a roller 108 carried at the free end of the lever 106 engages the necked-down portion 109 of a sleeve 110 pinned to the plunger at the end thereof contiguous to the lever and integral with the adjacent pressure head 94. Segments of the plunger sleeve 110 at opposite ends of the necked-down portion 109 are flared out to form two opposed cone shaped cams 111. Thus, upon movement of the plunger 92 to either side of its central position, as indicated in dotted lines in Fig. 7 or as shown in Fig. 3, one or the other of the cams 111 engages the roller 108 to pivot the lever 196 toward the clutch control plungers 60, 61. This swinging movement of the lever 106 is transmitted to the spool 101 by a projecting tip 112 on the free end of the lever which engages an enlarged flange 114 on the end of the spool adjacent the clutch control plungers '60, 61.

During the ensuing movement of the spool 101 from the position shown in Fig. 5 to that illustrated in Fig. 1,

the spool flange 114 engages the inner end of the one of the two clutch control plungers 60, 61 that was previously moved inwardly to engage the appropriate one of the clutches 39 to rotate the rollers 12, 14 in the desired direction. The plunger thus engaged by the spool flange 7 114 is carried back to its neutral position, Fig. 1, which action automatically moves the other of the two plungers 60, 61 inwardly to its neutral position. Hence, upon completion of its stroke, the spool is brought into positive engagement with both clutch control plungers 60, 61 to assure that neither of the power clutches 39 remains engaged.

The same longitudinal displacement of the intermediate control element 100 that disengages the wringer rollers from the power drive also serves to release the head 20 for upward movement which carries the upper roller 14 away from the lower roller 12. Thus, as an incident to left to right disabling movement of the control element spool 101 from the position shown in Fig. 5, to that of Fig. 1, a second spool flange 115, formed on the end of the spool remote from the first flange 114 engages the lower bifurcated end of the latching plate 80 which depends into straddling relation to the spool between the two flanges 114, 115. The spool flange 115 swings the latching plate 80 about its pivotal support away from the rock shaft collar 85 whereby the latching ledge 91 is moved beyond the tip of the collar finger 89 and out of latching engagement with the rock shaft 75.

Immediately after the rock shaft 75 is unlatched it is rotated reversely or counterclockwise, Figs. 6 and 7, t the position shown in Figs. 2, 4, and l to shift the head 20 upwardly. Quick reverse rota-tion of the rock shaft 75 to snap the upper roller 14 away from the lower roller 12 is assured by a spring pressed toggle lever 116 disposed along the inner face of the housing bulkhead 78 in a generally inclined attitude extending upwardly from left to right above the roller coupling 36 as viewed in Figs. 4 and 6. The lower end of the toggle lever 116 is pivoted at 117 between the lower portion of the bulkhead 78 and the support 34. The upper end of the lever 116 is connected by a link 119 to the free end of a radial arm 120 coupled to the rock shaft collar 85. The connecting link 119 is disposed between the rock shaft 75 and the toggle lever pivot 117 whereby clockwise movement of the lever, between the position of Fig. 6 and that of Fig. 4, induced by a compression spring 121 acting between one seat 122 on the medial portion of the lever and a second seat 124 on the opposing side wall 95 of the housing 22, produces the desired reverse or counterclockwise movement of the rock shaft 75.

It will be appreciated that the quick separation of the rollers 12, 14 from each other and the disconnection of the rollers from the power drive are achieved not only simultaneously, but also independently as a consequence of a single manual actuation of either of the pressure heads 94. Thus, the declutching of the engaged one of the clutches 39 by the spool 101 is effected directly by the manual action of the operator independently of upward movement of the head 20 following unlatching of the rock shaft 75. Similarly, the triggering of upward release movement of the head 20 is achieved by the manually induced movement of the spool, even though the engaged one of the clutches 39 should become jammed in engaged position.

In addition to disconnecting the wringer rollers from the power drive and triggering the upward shifting movement of the upper roller 14 to inoperative position, a single disabling stroke of the intermediate control element 100 also releases the upper roller 14 for lateral movement away from the lower roller 12. When the head 20 is in its lower or operative position, Fig. 5, the pointed end of the control spool carrier pin 102 which pierces the housing bulkhead 78 extends into a generally vertical kidney shaped aperture 125 defined in the adjacent leg 19 of the head. Thus, the head 20 is locked against pivotal movement about the rock shaft 75 to retain the upper roller directly above the lower roller 12. However, the carrier pin 102 is fixed to the control spool 101 whereby the disabling stroke of the latter retracts the pin from the aperture 125 to release the head 20 for 8 free horizontal swinging movement about the rock shaft 75 to further separate the upper roller 14 from the lower roller 12. a

The head 20 with the structural elements attached thereto is so balanced that upon removal of objects disposed between the wringer rollers the head swings into vertical position of its own accord. Then the wringer may be restored into full operation merely by pressing one or the other of the two control buttons 57 or 59,

depending on which direction of roller rotation is desired.

However, as a safety feature, restarting the wringer is positively precluded until the head 20 is properly positioned about the rock shaft to aline the locking aperture 125 in thehea d with the control element pin 102 thereby bringing the upper roller 14 into overlying relation to the lower roller 12. Thus, should an attempt be made to restart the wringer while the head 20 remains in a laterally pivoted position, inward clutch engaging movement of both of the clutch control plungers 60, 61 is blocked by the control spool 101 that is held against movement to the left, Fig. 1, by abutting engagement of the spool support pin 102 with the adjacent head leg 19 on one side of the aperture 125. But when the head 20 is in its normal position, the pin 102, upon inward movement of either clutch engaging plunger 60, 61, is slid freely into the lower end of the aperture 125 to lock the head 20 against lateral swinging movement concurrently with the engagement of the selected one of the power clutches 39.

Immediately after one of the power clutches 39 is reengaged, the upper wringer roller 14 is automatically reset into yieldable engagement with the lower roller 12 by energy derived from the power drive 15. For this purpose a circular cam 126 is eccentrically mounted on the coupling 36 to the lower roller 12 in medial alinement with the toggle lever 116, which is constructed from a pair of spaced plates 127 fixed in spaced relation to each other, Figs. 4 and 5. During the first revolution of the cam 126, after engagement of the roller'12 with the drive shaft 15, the cam engages a cam follower 129 on the toggle lever 116 to swing the lever upwardly in a counterclockwise direction from the position shown in Fig. 4 to that of Fig. 6. This motion of toggle lever 116 is transmitted into clockwise rotation of the rock shaft 75, Figs. 2, 4, and 6, to force the head 20 downwardly into operative position.

As shown in Fig. l, the pivotal support for the latching plate is so correlated with the rock shaft latching finger 89 that the plate, when in the unlatched position, is disposed in an inclined attitude over the finger. Thus, when the rock shaft 75 is rotated to lower the head 20 into operative position, the free end of the finger 89 slides upwardly in an inclined are along the contiguous portion of the latching plate 80. This swings the latching plate 80 slightly away from the collar until the finger 89 reaches the recess 90 in the plate just as the head 20 progresses to its operative position. Then the latching plate 80 is snapped toward the collar 85 by the spring 84 to engage the ledge 91 with the finger 89 to latch the rock shaft 75 against reverse movement, as previously described.

As a further safety feature, the linkage used for forceably lowering the head 20 to its operative position is made sensitive to any abnormal resistance to downward movement of the upper roller 14, such as might be presented by the continued presence between the rollers of objects likely to be damaged, to cut short the resetting cycle and return the rollers to their fully separated and de-energized condition.

For this purpose the resetting motion of the toggle lever 116, which when transmitted by the intermediate link 119 to the radial arm 120 forms a torque about the rock shaft 75, is transmitted to the rock shaft through a torque limiting coupling with the rock shaft collar 85; One element of this coupling 130 is formed by an 9 annular sleeve 131, Figs. and 6, integral with the radial arm 126 and encircling the rock shaft 75 at the end of the collar 85 remote from latching plate 80. The sleeve 131, itself, is freely rotatable on the rock shaft 75, but is held by a snap ring 132 on the shaft against axial movement away from the collar 85.

Roller resetting torque of the sleeve 131 is transmitted to the collar 85 by a tapered lug 134, Fig. 1, extending axially from the end face of the sleeve adjacent the collar 85 into a complementary trough shaped recess 135 in the opposing collar face. Because of the oblique disposition, relative to the rock shaft axis, of the coacting torque transmitting abutting surfaces on the lug 134 and the collar recess 135, the application of roller resetting torque to the collar 35 induces an axial camming force on the collar acting toward the latching plate 80. This axial force on the collar 35 is opposed by a spring 136, which in this instance is coiled about the rock shaft 75 between the collar and an annular abutment 137 on the adjacent end of the shaft.

In a normal roller resetting cycle the pressure of the spring 136 maintains the collar 85 in coupled engagement with the sleeve 131 whereby the action of the power resetting mechanism is transmitted to the rock shaft 75. However, in the event rotation of the rock shaft 75 is resisted to an unusual degree, as when the downward movement of the head is impeded abnormally, the axial camming force on the collar 85 increases to overcome the force of the spring 136. This allows some rotary slippage of the sleeve 131 relative to the collar 85 which forces the collar axially outward along the shaft 75 against the latching plate 80. It will be understood that axial movement of the collar 35 on the rock shaft 75 is permitted by the pin and slot connection 86, $7.

This axial movement of the collar 85 is transmitted by the finger 89 to the latching plate 80 to swing the latter further toward the clutch control plungers 60, 61. As a consequence, the lower end of the latching plate engages the collar 114 of the control spool 1G1 and carries it against the inwardly projecting one of the plungers 60, 61 to declutch the engaged one-of the clutches 39. This, of course, disconnects the lower roller 12 and the resetting cam 126 from the power drive. The pin 102 is retracted from the head 20 and since the head has not reached its operative position it is fully returned to its raised inoperative position by the toggle lever spring 121. As a consequence of this automatic action, the wringer is again returned to its fully disabled condition. Moreover, it then stands again in readiness to be restored to full operation in response to a single movement of one or the other of the control buttons 57, 59 as soon as the impediment to the downward movement of the head 20 has been removed.

To assure that snappy upward shifting movement of the head 20 will not be interfered with by the resetting cam 126, means are provided for shifting the cam follower 129 to a secondary position remote from the path of the cam once the wringer is placed in full operation. For this purpose, the cam follower 129, which is preferably of a roller type construction, is supported between the lower ends of a pair of spaced links 139. As shown in Figs. 4, 5, and 6, the links 139 extend upwardly between the toggle lever plates 127 from the roller follower 129 to a pivotal connection with the toggle plates. The links 139 are interconnected with the housing 22 by a double acting spring linkage 141 which in the present instance comprises a transverse rod 142 pivoted at one end of the housing and extending through two spaced flanges 144 of a cage 145 pivoted to the links. A helical spring 146 coiled about the rod 142 between the cage flanges 144 coacts with two spaced abutment pins 147 fixed to the rod and normally in registry with the respective cage flanges. Upon the application of longitudinal force to the rod 142 one or the other of the abutment pins 147 passes through the contiguous cage flange 144 to engage the adjacent end of the spring 146 which then biases the cam follower links 139 about the pivot 140.

Thus, when the toggle lever 116 is pivoted to its lower position to raise the head 20 to its upper position, the spring linkage 141 biases the links 139 toward the lever pivot 117 to dispose the cam follower 129 in the rotary path of the cam 126, Fig. 4. Upon engagement of the cam 126 with the follower 129 to return the head 20 to operative position, a member 149 on the lower end of the links 139 engages an abutment 150 on the toggle lever 116 to carry the lever in an upward extending are about its pivot 117. This compresses the cage spring 146, which becomes effective as soon as the cam 126 passes beyond the follower 129 to swing the links 139 away from the lever pivot 117 to dispose the follower in its secondary position, Fig. 6, out of the rotary path of the cam.

It will be appreciated that in the event the rock shaft is unlatched to separate the wringer rollers while the cam 126 is in an upper portion of its orbit of movement, the spring linkage 141 connected to the cam follower links 139 assures that downward swinging movement of the lever 116 is not interfered with by engagement of the cam follower 129 with the cam. Thus, the yieldable connection between the cage 145 and the rod 142 permits the follower to be swung by the cam toward its secondary position relative to the lever 116 without blocking movement of the lever. Once the cam 126 is rotated out of its upper position, the follower 129 is then snapped by the spring 146 into its operative position, Fig. 6.

Reverting to the mechanism used to control the power clutches 39, it will be perceived that once the wringer is put into operation the wringer rollers 12, 14 can be disconnected from the drive shaft 15 or reversed in their direction of rotation without being separated from each other by manual actuation of the outermost one of the control buttons 57, 59 independently of the disabling controls 94.

I claim as my invention:

1. A power reset wringer comprising, in combination, a frame including a base and a squeezing roller journaled in said base, a rock shaft mounted on said base in spaced generally parallel relation to said roller, a head journaling a roller thereon, said head being mounted on said rock shaft for shifting movement by the latter toward and away from said base section, power transmission means interconnected with one of said rollers and including a clutch therein, a power reset linkage interconnected with said rock shaft and coacting with said power transmission to forceably move said head toward said base section, a collar axially movable on said rock shaft and anchored for rotation therewith, a latching element on said collar, a latching plate movably mounted on said base and extending across said rock shaft, said plate defining a ledge thereon for coaction with said collar element to latch said rock shaft against roller separating movement, a disabling control having means operatively associated with said latching plate for unlatching said rock shaft and also having means operatively associated with said clutch for simultaneously disengaging said clutch, said latching plate having a portion in the path of axial movement of said collar for movement thereby and having a second portion positioned to actuate said clutch disengaging means upon movement of said latch plate by said collar, and torque responsive means interconnecting said power reset means with said rock shaft collar for producing axial movement of the latter against said latching plate in the event power movement of said head toward said base section meets with abnormal resistance thereby moving said latch plate to automatically disengage said clutch.

2. A power reset wringer comprising, in combination, a frame including a base section having a squeezing roller journaled thereon, a rock shaft mounted on said 11 base section in parallel spaced relation to said roller, a head section having a second squeezing roller journaled thereon, said head section being supported on said-rock shaft for movement toward said base section in response to forward rotary movement of said rock shaft to engage said rollers, and away from said base section in response to reverse rotary movement of said rock shaft to separate said rollers, power transmission means interconnected with one of said rollers and including a clutch therein, power reset linkage interconnected with said rock shaft and coacting with said power transmission to forceably rotate said rock shaft to carry said head section into operative position, a torque limiting coupling interconnected between said power reset linkage and said rock shaft to limit the maximum resetting force applicable to said head section, and means interconnecting said coupling with said clutch for causing automatic disengagement thereof in the event power movement of said head section toward said base section meets with abnormal resistance.

3. A power reset wringer comprising, in combination, a frame including a base section having a squeezing roller journaled thereon, a rock shaft mounted on said base section in parallel spaced relation to said roller, a head section having a second squeezing roller journaled thereon, said head section being supported on said rock shaft for movement toward and away from said base section to engage and separate said rollers in response to forward and reverse rotary movement respectively of said rock shaft, power transmission means interconnected with one of said rollers, power reset linkage interconnected with said rock shaft and coacting with said power transmission to forceably rotate said rock shaft to carry said head section into operative position, and a torque limiting coupling including resiliently biased clutch elements interconnected between said power reset linkage and said rock shaft to limit the maximum resetting force applicable to said head section.

4. A power reset wringer comprising, in combination, a frame section and a movable section mounted thereon, squeezing rollers journaled in said respective sections, shifting means interconnected between said sections for shifting said movable section toward and away from said base section to disengage and separate said rollers, a power transmission interconnected with one of said rollers and including a clutch therein, a power reset linkage connected to said shifting means and arranged for coaction said said power transmission means to forceably shift said movable section into said operative position, declutching means interconnected between said power reset means and said clutch, and torque responsive actuating means coacting with said power reset means and said shifting means and interconnected with said de-clutching means to disengage said clutch in the event return movement of said head section into said operative position meets with abnormal resistance.

5. A power operated wringer comprising, in combination, a frame including a base section having a squeezing roller journaled therein, a rock shaft mounted on said base section in general parallel spaced relation to said roller, a head section swingably mounted on said rock shaft, a control mechanism housing disposed at one end of said frame, a power shaft protruding into said housing, a transmission interconnecting said power shaft with one of said rollers and having a clutch interposed therein, biasing means acting on sm'd rock shaft to shift said head section outwardly of said base section into an inoperative position, latching means on said rock shaft for retaining said head section in an operative position inwardly of said inoperative position, movable retaining means in said housing engageable with said head for releasable preventing lateral swinging movement of said head, triple action disabling means mounted in said housing, first separate linkage means interconnecting said disabling means with said clutch for disengaging said clutch independently of movement of said head section, second separate linkage means interconnecting said disabling means with said latching means for disengaging said latching means, a third separate linkage interconnecting said disabling means and said retaining means for moving the latter to release position, and disabling control means accessibly located on said frame and interconnected with said disabling means to actuate the latter for concurrently disengaging said clutch and said latching means and unlocking said head for lateral swinging movement about said rock shaft.

6. A power reset wringer comprising, in combination, a frame including a base and a squeezing roller journaled in said base, shifting means including a rock shaft mounted on said base and having an axially movable collar thereon, a head journaling a squeezing roller thereon, said head being mounted on said shifting means for movement by the latter toward and away from said base section, power transmission means interconnecting with one of said rollers and including a clutch therein, a power reset linkage connected with said shifting means and powered by said power transmission to forceably move said head toward said base section, latch means for releasably re-- taining said head in operative position, a disabling control having means interconnected with said clutch for disengaging the latter and also having means operatively associated with said latch means for unlatching said head, said latch means positioned to be engaged and moved in the direction of unlatching movement by said collar upon axial movement of the latter, said latch means having a portion for actuating said clutch disengaging means upon movement of said latch means, and torque responsive means interconnecting said power reset means and said rock shaft for producing axial movement of said collar for automatically disengaging said clutch in the event that power movement of said head toward said base meets with abnormal resistance.

7. A power reset wringer comprising, in combination, a frame including a base having a squeezing roller journaled thereon, a head having a squeezing roller journaled thereon, means for mounting said head on said frame for movement into and out of operative roller engaging position, power transmission means including a clutch for driving one of said rollers, a control for shifting said clutch into neutral and drive positions, a power reset. linkage connected to the output of said power transmis-.

sion means for moving said head into operative position,

said linkage including a torque responsive coupling having a pair of members movable relative to each other upon meeting abnormal resistance in power movement of said head to operative position, and means for transmitting relative movement between said relatively movable torque responsive members to' said clutch control for moving said clutch to neutral when abnormal resistance is met in power movement of said head to operative position.

8. A power driven wringer of the character described comprising, in combination, a frame including a base section having a first roller journaled thereon, a head section having a second roller journaled thereon, shifting means' including a rock shaft rotatably mounted on said base and connected to said head for moving the latter to operative and inoperative positions upon forward and reverse rotation, respectively, of said shaft, power driving means including a clutch for driving one of said rollers,

latching means including a movable latch for holding said rock shaft in forwardly rotated position to releasably maintain said head in operative position, a disabling control mounted on said frame, a manual clutch control having resilient linkage means interconnecting said manual control with said clutch and movable to neutral and drive positions, first separate linkage means interconnecting said disabling control with said manual clutch control for moving the latter to neutral positions independently of movement of said head, and a second linkage means interfor releasing said head independently of the declutching therewith.

References Cited in the file of this patent UNITED STATES PATENTS Barnes Dec. 8, 1925 Wood Oct. 14, 1930 Behan Aug. 4, 1931 Starkey et a1 Aug. 18, 1931 14 Geldhof July 28, 1936 Hoke Nov. 14, 1939 Perkins Aug. 13, 1940 Altorfer Feb. 11, 1941 Kauifman Jan. 6, 1942 Schroeder July 7, 1942 Parish Aug. 4, 1942 Ferris Sept. 17, 1946 

